EP3803129B1 - Laufrad-lufteinlassschnittstelle für einen kreisellüfter, sowie kreisellüfter damit - Google Patents

Laufrad-lufteinlassschnittstelle für einen kreisellüfter, sowie kreisellüfter damit Download PDF

Info

Publication number
EP3803129B1
EP3803129B1 EP18746744.4A EP18746744A EP3803129B1 EP 3803129 B1 EP3803129 B1 EP 3803129B1 EP 18746744 A EP18746744 A EP 18746744A EP 3803129 B1 EP3803129 B1 EP 3803129B1
Authority
EP
European Patent Office
Prior art keywords
air intake
impeller
inlet shroud
inlet
interface
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP18746744.4A
Other languages
English (en)
French (fr)
Other versions
EP3803129A1 (de
Inventor
Gaël Herve
Francette FOURNIER
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Carrier Corp
Original Assignee
Carrier Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Carrier Corp filed Critical Carrier Corp
Publication of EP3803129A1 publication Critical patent/EP3803129A1/de
Application granted granted Critical
Publication of EP3803129B1 publication Critical patent/EP3803129B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F04D29/162—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of a centrifugal flow wheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4226—Fan casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/51—Inlet

Definitions

  • Embodiments of the disclosure relate to a centrifugal fan, and more particularly, to the configuration of the flow path defined between the inlet shroud of an impeller and the inlet bell of an air intake.
  • Centrifugal fans are typically used in ventilation and air conditioning systems.
  • Examples of common types of ventilation and air conditioning units include, but are not limited to, cassette type ceiling fans, air handling units, and extraction roof fans for example. Air is sucked into the unit and guided by a bell mouth intake into an impeller. A diameter of the bell mouth intake at the interface between the bell mouth intake and the inlet shroud of an impeller is smaller than a diameter of the blower at the interface. Accordingly, a clearance in fluid communication with the blower exists between the exterior of the bell mouth intake and the interior of the blower. A portion of the air output from the blower may recirculate to the impeller through this clearance, thereby reducing the operational efficiency of the fan, and increasing a noise level thereof.
  • WO 2006/106744 A1 discloses a centrifugal blower which has an impeller, a casing receiving the impeller and forming a spiral flow path radially outside the impeller, and a drive device for rotatingly driving the impeller about an axis.
  • the impeller is constructed from a bottom plate, blades arranged on the same circumference of the bottom plate, and a shroud of a substantially annular plate shape, installed coaxial with the bottom plate with the blades positioned between the shroud and the bottom plate.
  • the shroud is composed of an inclination section approaching the bottom plate as it goes from the radially inside to the radially outside of the shroud, and a shroud side barrier wall rising from a position more radially outside than the inclination section to the opposite side of the bottom plate.
  • the casing is provided with a bell mouth open at a position more on the radially inside than an inner peripheral edge of the shroud, and with a casing side barrier wall projecting in the region between the inner peripheral edge of the shroud and the shroud side barrier wall.
  • the centrifugal fan or blower 10 includes a fan motor, illustrated schematically at 20, and an impeller 30.
  • the fan motor 20 includes a motor base 22 and a motor shaft 24 extending from the motor base 22 and configured to rotate about an axis X.
  • the impeller 30 is mounted to the motor shaft 24 for rotation with the shaft 24 about the fan axis X.
  • the impeller 30 includes a plurality of fan blades 32 that are connected at a distal end via an inlet shroud 34.
  • the centrifugal fan 10 additionally includes an air intake 40.
  • the air intake 40 is typically formed with a bell mouth, and is always arranged upstream from the inlet shroud 34 relative to the flow of air A through the centrifugal fan 10.
  • the air intake 40 includes a first end 42 and a second end 44, the second end 44 being substantially coplanar with, or alternatively, slightly overlapping an inlet end 36 of the inlet shroud 34.
  • the air intake 40 has a first diameter at the first end 42 and a second diameter at the second end 44 thereof, the second diameter being substantially smaller than the first diameter, and smaller than the diameter of the inlet shroud 34 at the inlet end 36.
  • the diameter of the air intake 40 gradually reduces between the first and second ends 42, 44 to achieve a desired curved shaped.
  • the fan motor 20 is energized, causing the impeller 30 to rotate about the axis X. This rotation sucks air into the impeller 30 via the intake 40, in the direction indicated by arrow A.
  • the axial air flow transitions to a radial air flow and is provided outwardly to an adjacent component, as indicated by arrows B, such as a heat exchanger (not shown) for example.
  • a clearance 46 exists between the exterior surface 48 of the air intake 40 and the interior surface 38 of the inlet shroud 34 of the impeller 30.
  • FIGS. 2-5 various examples of the clearance 46 formed between the air intake 40 and the inlet shroud 34 of an impeller 30 of a centrifugal fan 10 having a configuration intended to minimize the leakage flow are illustrated.
  • the internal profile of the inlet shroud 34 is similar to the inlet shroud of existing systems.
  • the inlet shroud 34 has a generally arcuate contour such that a diameter of the inlet shroud 34 gradually increases in the axial direction of the airflow A.
  • a secondary flange 50 extends from an exterior surface of the inlet shroud 34 at a generally central portion thereof.
  • the flange 50 may be oriented substantially parallel to the rotational axis X of the impeller 30. Due to the curvature of the inlet shroud 34, a portion of the inlet shroud 34 extending between the flange 50 and the inlet end 36 may also be oriented generally parallel to the flange 50. As a result, a clearance 52 is defined between the flange 50 and the portion of the inlet shroud 34 extending between the flange 50 and the inlet end 36 of the shroud 34. Accordingly, in an embodiment, the inlet shroud 34 may be considered to have a Y-like shape adjacent the inlet end 36 thereof.
  • the free end 54 of the flange 50 may extend a distance beyond the upstream end 40 of the inlet shroud 34. Further, the free end 54 of the flange 50 and the adjacent end 36 of the inlet shroud 34 are beveled, such as at an angle towards the central axis X about which the inlet shroud 34 rotates. This angle may be intended to direct the remaining leakage flow provided to the impeller 30, as close to parallel with the rotational axis X as possible.
  • the inlet shroud 34 including the flange 50 is formed via a molding process using a composite material.
  • the air intake 40 is defined by a thin piece of material, such as sheet metal for example, contoured to form a bell mouth shape.
  • the air intake 40 includes a generally axisymmetric body 60 defined by a linearly extending sidewall 62.
  • a minimum thickness of the sidewall 62 may be determined by the manufacturing process used to form the air intake 40.
  • the minimum thickness of the sidewall 62 of the suction intake 40 is sized to be compatible for manufacturing using a material such as expanded polystyrene or "PSE.” Further, the maximum thickness may be determined by the free space within the centrifugal fan 10.
  • the air intake 40 additionally includes a curved bell mouth contour 64 to facilitate the flow of air towards the impeller 30.
  • the bell mouth contour 64 is integrally formed with the inlet end 66 of the sidewall 62.
  • a distal end 68 of the bell mouth contour 64 is offset from the adjacent surface of the sidewall 62.
  • a gap 70 is defined between the distal end 68 of the bell mouth contour 64 and the sidewall 62.
  • the clearance 80 extends between the exterior and the interior of the fan 10 to define a fluid flow path through which leakage flow may recirculate to the impeller 30.
  • the fluid flow path defined by the clearance 80 is a generally tortuous, non-linear flow path having one or more turns.
  • the flow path defined by the clearance 80 may function in a manner similar to a labyrinth seal to prevent or restrict air from recirculating through the impeller 30.
  • the air output radially from the impeller 30 makes a first turn, indicated by arrow C1, to enter the clearance 80 defined between the air intake 40 and the inlet shroud 34.
  • the leakage flow must travel generally parallel to the sidewall 62 of the air intake 40 and the axis of rotation X until reaching distal end 54 of flange 50.
  • the leakage flow is configured to make a second turn, indicated by arrow C2, around the distal end 54 of the flange 50 and the inlet end 36 of the inlet shroud 34 located within the gap 70.
  • This second turn C2 redirects the leakage flow by at least 90 degrees, and in some embodiments, by 120 degrees, by 150 degrees, up to 180 degrees.
  • the outlet of the fluid flow path adjacent the downstream end 80 of the bell mouth 64 is oriented generally parallel to the main inlet airflow A.
  • the configuration of the inlet shroud 34 and the air intake 40 is substantially identical to those illustrated and described with respect to FIGS. 2A and 2B .
  • the clearance 80 and fluid flow path defined by the clearance 80 is substantially identical between FIGS. 2A & 2B, and FIGS. 3A and 3B .
  • the distal end 68 of the bell mouth curve 64 is pointed, rather than being rounded.
  • the overall length of the bell mouth curve 64 is shorter than in the previous embodiment.
  • the end 68 of the bell mouth curve 64 ends at a location between ends 54, 36 of the flange 50 and the inlet shroud 34, respectively.
  • the bell mouth curve 64 extended further to a position adjacent the inlet end 36 of the inlet shroud 34.
  • the inlet shroud 34 includes a first portion 56 having a generally axial contour and second portion 58 having an arcuate contour.
  • the first portion 56 of the inlet shroud 34 extends linearly, such as in a vertically oriented axis for example, from the inlet end 36 of the inlet shroud 34.
  • the axial length of the first axial portion 56 measured generally parallel to the axis of rotation X, may be generally equal to, greater than, or alternatively, less than the axial length of the second arcuate portion 58 of the inlet shroud 34.
  • the axial portion 56 of the inlet shroud 34 typically extends vertically below the second end 68 of the air intake 40.
  • the bell mouth contour 64 shown in FIGS. 2-3 is integrally formed with the sidewall 62
  • the bell mouth contour 64 including the distal end 68 thereof, is formed by a separate component 72 removably or permanently coupled to the sidewall 62.
  • the inlet shroud 34 and the air intake 40 cooperate to form a clearance 80 there between.
  • the clearance 80 defines a fluid flow path through which leakage flow may recirculate to the impeller 30.
  • the air output radially from the impeller 30 makes a first turn, indicated by arrow C1, to enter the clearance 80 defined between the air intake 40 and the inlet shroud 34.
  • the leakage flow must travel generally parallel to the sidewall 62 of the air intake 40 and the axis of rotation X until reaching distal end 36 of the axial portion 56 of the inlet shroud 34.
  • the leakage flow is configured to make a second turn, indicated by arrow C2, around the distal end 36 of the axial portion 56 and the inlet end 36 of the inlet shroud 34 located within the gap 70.
  • This second turn C2 redirects the leakage flow by at least 90 degrees, and in some embodiments, by 120 degrees, by 150 degrees, up to 180 degrees.
  • the outlet of the fluid flow path adjacent the downstream end 68 of the bell mouth 64 is oriented generally parallel to the main inlet airflow A.
  • the external shape of the inlet shroud 34 is similar to the embodiment of FIGS. 4A and 4B .
  • the inlet shroud 34 has a first portion 56 having a generally axial contour and second portion 58 having an arcuate contour.
  • a thickness of the axial portion 56 varies over the axial length of the axial portion 56.
  • the thickness of the axial portion 56 of the inlet shroud 34 gradually increases from adjacent the interface with the second portion 58 towards a center of the axial portion 56.
  • the thickness of the axial portion 56 gradually increases from adjacent the inlet end 36 of the inlet shroud 34 towards the center of the axial portion 56.
  • the resulting thickness variation has a generally triangular-shaped contour.
  • the exterior surface 59 of the first, axial portion 56 maintains a linear configuration such that the variation in thickness is formed at an interior facing side of the first portion 56 of the inlet shroud 34.
  • the separate component 72 of the air intake 40 defines only a portion of the bell mouth contour 64, such as the distal end 68 thereof. As shown, the component 72 extends linearly, such as in a vertically oriented axis for example, parallel to axis X. The component 72 is offset from both the sidewall 62 such that the end 36 of the inlet shroud 34 is receivable within the gap 70 defined between the component 72 and the sidewall 62.
  • the fluid flow path defined by the clearance 80 formed between the air intake 40 and the inlet shroud 34 is similar to that taught in the embodiment of FIGS. 4A and 4B .
  • the fluid flow path makes an additional turn, illustrated by arrow C3, resulting from the thickness variation in the first axial portion 56 of the inlet shroud 34.
  • the turn C3 redirects the leakage flow by at least 30 degrees, and in some embodiments, by 45 degrees, or by up to 60 degrees, such that the outlet of the fluid flow path adjacent the downstream end 68 of the bell mouth 64 is oriented generally parallel to the main inlet airflow A.
  • the contour of the gap 80 may be generally complementary in size and shape to a portion of the inlet shroud 34 receivable therein.
  • the amount of leakage flow returned to the impeller 30 is reduced. Further, by orienting the leakage flow generally parallel to the rotational axis X as it reenters the impeller 30, the remaining leakage flow will deviate as little as possible the main flow toward the axis, preventing an inhomogeneous velocity profile at the inlet section of the impeller 30. The improvement in efficiency achieved by reducing the leakage flow and directing the leakage flow within the impeller 30 will result in a lower noise level of the fan 10.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (11)

  1. Schnittstelle für einen Zentrifugallüfter (10), umfassend:
    eine Einlassabdeckung (34) eines Laufrads (30);
    einen Lufteinlass (40), der in überlappender Anordnung mit einem Teil der Einlassabdeckung (34) angeordnet ist; und
    einen Zwischenraum (52), der zwischen der Einlassabdeckung (34) und dem Lufteinlass (40) definiert ist, wobei der Zwischenraum (52) einen Labyrinth-Fluidströmungsweg für einen Leckluftstrom bildet;
    wobei sich ein Flansch (50) von einer Außenfläche der Einlassabdeckung (34) an einem allgemein mittleren Abschnitt desselben erstreckt; und
    dadurch gekennzeichnet, dass das freie Ende (54) des Flansches (50) und ein benachbartes Ende (36) der Einlassabdeckung (34) in einem Winkel zur Mittelachse X, um die sich die Einlassabdeckung (34) dreht, abgeschrägt sind.
  2. Schnittstelle nach Anspruch 1, wobei der Labyrinth-Fluidströmungsweg eine nichtlineare Konfiguration aufweist, oder wobei der Zwischenraum (52), der den Labyrinth-Fluidströmungsweg bildet, mindestens eine darin ausgebildete Windung aufweist.
  3. Schnittstelle der zweiten Option von Anspruch 2, wobei die mindestens eine Windung mindestens eine 90-Grad-Windung umfasst, wobei optional die mindestens eine Windung mindestens eine 120-Grad-Windung ist, oder wobei die mindestens eine Windung etwa eine 180-Grad-Windung ist.
  4. Schnittstelle nach einem der vorhergehenden Ansprüche, wobei der Lufteinlass (40) einen Spalt (70) aufweist, der darin ausgebildet ist, und ein Teil der Einlassabdeckung (34) innerhalb des Spalts (70) so angeordnet ist, dass sich der Lufteinlass (40) und die Einlassabdeckung (34) axial überlappen.
  5. Schnittstelle nach Anspruch 4, wobei der Spalt (70) zwischen einer Seitenwand (62) des Lufteinlasses (40) und einem Teil einer Glockenmundkurve eines Saugeinlasses (40) angeordnet ist.
  6. Schnittstelle nach Anspruch 5, wobei der Lufteinlass (40) einen achsensymmetrischen Körper (60) umfasst, der durch die Seitenwand (62) definiert ist.
  7. Schnittstelle nach einem der vorhergehenden Ansprüche, wobei der Flansch (50) im Wesentlichen parallel zur Rotationsachse des Laufrads (30) ausgerichtet ist.
  8. Schnittstelle nach Anspruch 5, wobei ein Spalt (70) zwischen dem distalen Ende (68) des Glockenkurvenabschnitts (64) und der Seitenwand (62) definiert ist, und wobei das Einlassende (36) der Einlassabdeckung (34) und das distale Ende (54) des Flansches (50) innerhalb des definierten Spalts (70) angeordnet sind, wobei sich der Flansch (50) optional weiter innerhalb des Spalts (70) in Bezug auf das Einlassende (36) erstreckt.
  9. Lüfter (10) mit einer Schnittstelle nach Anspruch 1, umfassend:
    ein Zentrifugallaufrad (30), das so konfiguriert ist, dass es sich um eine Rotationsachse dreht, wobei das Laufrad (30) eine Vielzahl von Schaufeln (32) und eine Einlassabdeckung (34) aufweist, die an einem distalen Ende der Vielzahl von Schaufeln (32) angebracht ist; und
    einen Lufteinlass (40), der vor dem Laufrad (30) relativ zu einem Hauptluftstrom angeordnet ist, wobei der Lufteinlass (10) so geformt ist, dass er den Hauptluftstrom auf das Laufrad (30) richtet; und
    einen Fluidströmungsweg, der zwischen dem Laufrad (30) und dem Lufteinlass-Saugeinlass (40) definiert ist, wobei der Fluidströmungsweg eine Labyrinthdichtung bildet.
  10. Lüfter nach Anspruch 9, bei dem der Fluidströmungsweg eine nichtlineare Konfiguration aufweist, wobei der Fluidströmungsweg optional mindestens eine darin ausgebildete Windung aufweist oder der Fluidströmungsweg mindestens eine Windung von etwa 180 Grad umfasst.
  11. Lüfter nach Anspruch 9, wobei der Lufteinlass (40) einen darin ausgebildeten Spalt (70) aufweist und ein Teil der Einlassabdeckung (34) innerhalb des Spalts (70) positioniert ist, wobei der Lufteinlass (40) optional ferner eine Seitenwand (62) und eine Glockenmundkurve umfasst, wobei der Spalt (70) zwischen der Seitenwand (62) und einem Teil der Glockenmundkurve (64) definiert ist.
EP18746744.4A 2018-06-11 2018-06-11 Laufrad-lufteinlassschnittstelle für einen kreisellüfter, sowie kreisellüfter damit Active EP3803129B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/IB2018/000749 WO2019239174A1 (en) 2018-06-11 2018-06-11 Impeller-air intake interface for a centrifugal fan, and centrifugal fan therewith

Publications (2)

Publication Number Publication Date
EP3803129A1 EP3803129A1 (de) 2021-04-14
EP3803129B1 true EP3803129B1 (de) 2024-03-27

Family

ID=63042062

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18746744.4A Active EP3803129B1 (de) 2018-06-11 2018-06-11 Laufrad-lufteinlassschnittstelle für einen kreisellüfter, sowie kreisellüfter damit

Country Status (4)

Country Link
US (1) US11460039B2 (de)
EP (1) EP3803129B1 (de)
CN (1) CN112236598B (de)
WO (1) WO2019239174A1 (de)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3647603A1 (de) 2018-10-31 2020-05-06 Carrier Corporation Anordnung eines radiallaufrads eines lüfters zur geräuschverminderung
GB2606558B (en) * 2021-05-13 2024-02-28 Dyson Technology Ltd A compressor
GB2606557A (en) * 2021-05-13 2022-11-16 Dyson Technology Ltd A compressor

Family Cites Families (36)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2778958A (en) 1954-10-28 1957-01-22 Gen Electric Dynamoelectric machine
US4917572A (en) * 1988-05-23 1990-04-17 Airflow Research And Manufacturing Corporation Centrifugal blower with axial clearance
JP3240854B2 (ja) 1994-09-26 2001-12-25 三菱電機株式会社 空気調和機の吹出口
US5743710A (en) * 1996-02-29 1998-04-28 Bosch Automotive Motor Systems Corporation Streamlined annular volute for centrifugal blower
JP3601807B2 (ja) 1997-10-08 2004-12-15 本田技研工業株式会社 自動２輪車用ラジエタ冷却装置
KR100392302B1 (ko) 1998-03-30 2003-07-22 다이킨 고교 가부시키가이샤 흡기·송풍 장치
EP1166018B1 (de) 2000-01-28 2004-11-10 Toshiba Carrier Corporation Kassettenartige klimaanlage zur deckenmontage
AU2001269822A1 (en) 2000-06-15 2001-12-24 Greenheck Fan Corporation In-line centrifugal fan
US6450765B1 (en) * 2000-06-19 2002-09-17 Caterpillar Inc. Sealing system for a centrifugal fan
JP2002022210A (ja) 2000-07-11 2002-01-23 Daikin Ind Ltd 空気調和装置
KR100405982B1 (ko) 2001-02-12 2003-11-14 엘지전자 주식회사 천정형 공조기의 유로 구조
KR100405981B1 (ko) 2001-02-12 2003-11-14 엘지전자 주식회사 천정형 공조기의 터보팬 구조
KR100459180B1 (ko) 2002-01-03 2004-12-03 엘지전자 주식회사 터보팬용 벨마우스
JP2004092583A (ja) * 2002-09-03 2004-03-25 Japan Servo Co Ltd 遠心ファン
JP4831811B2 (ja) * 2005-03-31 2011-12-07 三菱重工業株式会社 遠心式送風装置
US7883312B2 (en) * 2005-03-31 2011-02-08 Mitsubishi Heavy Industries, Ltd. Centrifugal blower
KR101229343B1 (ko) 2005-12-29 2013-02-05 삼성전자주식회사 천장형 공기조화기
CN101395381B (zh) 2006-03-29 2012-05-30 东芝开利株式会社 涡轮风扇和空调机
KR100782197B1 (ko) 2006-08-03 2007-12-04 엘지전자 주식회사 공기 조화기
JP4865497B2 (ja) * 2006-10-19 2012-02-01 三菱重工業株式会社 遠心式送風装置
WO2008111372A1 (ja) 2007-03-14 2008-09-18 Mitsubishi Electric Corporation 空気調和機
KR101160401B1 (ko) 2007-10-25 2012-06-26 도시바 캐리어 가부시키가이샤 천정 매입형 공기 조화기
JP4844678B2 (ja) 2010-02-10 2011-12-28 ダイキン工業株式会社 遠心送風機
JP2014118949A (ja) 2012-12-19 2014-06-30 Panasonic Corp 自吸式遠心ポンプ
KR102199376B1 (ko) 2013-07-12 2021-01-06 엘지전자 주식회사 원심 송풍기 및 이를 포함하는 공기 조화기
JP6233128B2 (ja) 2014-03-25 2017-11-22 株式会社富士通ゼネラル 天井埋込型空気調和機
CN106461264B (zh) 2014-06-13 2019-06-21 三菱电机株式会社 天花板嵌入型空调机
EP3193097B1 (de) 2014-09-30 2023-08-23 Daikin Industries, Ltd. Inneneinheit für eine klimaanlage
JP6369684B2 (ja) 2014-10-10 2018-08-08 株式会社富士通ゼネラル 天井埋込型空気調和機
US9664058B2 (en) 2014-12-31 2017-05-30 General Electric Company Flowpath boundary and rotor assemblies in gas turbines
CN204402918U (zh) 2015-01-29 2015-06-17 宁波巨神制泵实业有限公司 大型潜水电泵防转防抬防晃动一体化装置
JP6504349B2 (ja) 2015-03-31 2019-04-24 株式会社富士通ゼネラル 天井埋込型空気調和機
JP6103154B1 (ja) 2015-06-12 2017-03-29 三菱電機株式会社 天井埋込型空気調和機
CN105275884B (zh) 2015-08-15 2019-11-29 何家密 动力式叶泵的增强及其应用
JP6704695B2 (ja) 2015-09-01 2020-06-03 日立ジョンソンコントロールズ空調株式会社 空気調和機の室内機
CN205315287U (zh) 2015-11-25 2016-06-15 天津市明奥泵业有限公司 一种防堵的污水泵

Also Published As

Publication number Publication date
WO2019239174A1 (en) 2019-12-19
CN112236598A (zh) 2021-01-15
EP3803129A1 (de) 2021-04-14
CN112236598B (zh) 2022-12-16
US20210246905A1 (en) 2021-08-12
US11460039B2 (en) 2022-10-04

Similar Documents

Publication Publication Date Title
EP3803129B1 (de) Laufrad-lufteinlassschnittstelle für einen kreisellüfter, sowie kreisellüfter damit
EP2980412A1 (de) Elektrisches gebläse
EP3452727B1 (de) Einlass für axiallüfter
CN105992877B (zh) 轴流鼓风机
JP6332546B2 (ja) 遠心送風機
CN106884804B (zh) 离心式鼓风机
US10907655B2 (en) Multiblade fan
US11566634B2 (en) Arrangement of centrifugal impeller of a fan for reducing noise
US20240026899A1 (en) Multi-blade centrifugal air-sending device
US10473113B2 (en) Centrifugal blower
JP2009275524A (ja) 軸流送風機
CN108087298A (zh) 一种用于车辆的鼓风机总成
US11261871B2 (en) Dual stage blower assembly
CN112400066A (zh) 送风机
JP7487854B1 (ja) 送風機
WO2022153522A1 (ja) 遠心送風機
JP7161654B2 (ja) 送風機
US20230243365A1 (en) Multi-blade centrifugal air-sending device
EP4098886A1 (de) Zentrifugalverdichter
US20220372990A1 (en) Impeller, multi-blade fan, and air-conditioning apparatus
EP3486495A1 (de) Zentrifugalgebläse mit mehreren schaufeln
CN113439163A (zh) 离心送风机及使用离心送风机的空调机
WO2015004751A1 (ja) 多翼送風機
JPH1182366A (ja) 遠心送風機

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: UNKNOWN

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20201217

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

17Q First examination report despatched

Effective date: 20220314

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20231206

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602018067160

Country of ref document: DE

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D